Thread-advancing reel



Oct. 23, 1951 A. J. L. MORITZ 2,572,181

THREAD-ADVANCING REEL Filed June 14, 1948 '7 Sheets-Sheet l g wuemtoc Oct. 23, 1951 J o z 2,572,181

THREAD-ADVANCING REEL Filed June 14, 1948 '7 Sheets-Sheet 2 Oct. 23, 1951 A. J. L MORITZ 2,572,181

THREAD-ADVANCING REEL Filed June 14, 1948 7 Sheet-Sheet 3 Oct. 23, 195] L, MORITZ 2,572,181

THREAD-ADVANCING REEL Filed June 14, 1948 7 Sheets-Sheet 4 Oct. 23, 1951 y A. J. L, MORITZ 2,572,181

THREAD-ADVANCING REEL Filed June 14, 1948 v 7 Sheets-Sheet 5 Oct. 23, 1951 A. J. L. MORITZ 2,572,131

THREAD-ADVANCING REEL Filed June 14, 1948 7 Sheets-Sheet 6 Oct. 23, 1951 A. J. L. MORITZ 2,572,181

' THREAD-ADVANCING REEL- Filed June 14, 1948 "7 Sheets-Sheet 7 wwzw Patented Oct. 23 1951 THREAD-ADVAN GIN G REEL Adrian J. L. Moritz, Enka, N. 0., assignor to American Enka Corporation, Enka, N. 0., a corporation of Delaware Application June 14, 1948, Serial No. 32,949

9 Claims. 1

This invention relates to thread-storage, thread-advancing devices and more particularly to a reelor cage-like device for storing and advancing thread in a manner compatible with such after-treatments as may be required in any particular process.

In the art of after-treatin wet spun rayon, the use of thread-storage, thread-advancing devices has become quite common and a large number of reel-like structures, designed for supporting and advancing thread during such treatments, have been developed.

In general, the reelor cage-like thread-storage, thread-advancing device is characterized by a plurality of circumferentially-spaced threadsupporting rods which are arranged so that first one group of the rods supports the thread and then the other. If the groups of rcds or units are arranged on converging axes, this transfer will cause thread wound on the reel or cage to progress in a generally helical path in the direction of convergence of the axes. If the two units or groups of rods are arranged on parallel axes, however, it is necessary to provide some sort of mechanism for reciprocating the threadadvancing rods and for causing them to contact the thread as they move in one direction and to recede from contact with the thread as they move in the other direction.

In general, the reel characterized by groups of rods arranged on convergent axes has met with greater success than the reciprocating-rod type due largely to the fact that reels of the latter type. as heretofore constructed, involved too many parts, were too difiicult to protect from It is a more specific object of this inventionto invention that the moving-parts of the threadstorage, thread-advancing unit be so located and constructed that they are fully protected from the action of any treating liquid sprayed onto thread supported on and advanced alon the unit.

It is another object of this invention to provide for correlated movements of a group of the componeut rods of a unit in a circular path in a plane normal to the long axes thereof, and in another circular path in the plane of the long axes thereof at any desired frequency while atfording frequency control that is wholly'independent of the take-up rate of the reel.

Other objects and advantages of this invention will be apparent upon consideration of the following detailed description of a preferred embodiment thereof in connection with the annexed drawings wherein:

Figure 1 is a view in side elevation of a threadstorage thread-advancing device constructed in accordance with the principles of the present invention, the position of thread supported and advanced thereon being shown;

Figure 2 is a view in vertical section of the thread-storage, thread-advancing device of Figure 1, the thread being removed in the'interest of convenience of illustration;

Figure 3 is an end view, partially in elevation and partially in section, taken along the line 3-3 of Figure 2;

Figure 4 is a developed view of the rod reciprocating cams used in the assembly shown in Figures 1, 2 and 3;

Figures 5, 6, '7 and 8 are views in cross section taken on the line 5-5 of Figure 1 at various stages in a single cycle of rod movement: and

Figures 9, 10, 11 and 12 are views in section taken along the line 9-9 of Figure 1 at stages in the cycle of operation corresponding respectively to the stages of Figures 5, 6, 7 and 8.

Referring now in greater detail to the drawings, and more particularly to Figures 1 to 5, inclusive, thereof, the numeral 10 represents a circular plate supporting a number of rods II in fixed relative relation, mutually parallel, and spaced circumferentially about a zone near the periphery of the plate. The rods ll extend to the left of plate 10 as it is shown in Figure 1, and together define an elongate cage of polygonal cross section the contour of which can be seen upon reference to Figures 3 and 5. In between the rods I I, there are mounted a plurality of rods 12, each rod l2 bein -supported from two points by connecting links l3 and I 4. Each of the connecting links I3 is pivotally connected at one end 3 to the respective rod I2. For this purpose an elongate cavity I5 is provided in the inner face of each rod I2 and a wrist pin I5 is passed through the rod and link to effect the pivotal connection. The other end of each link I3 is attached to or formed with aball-like cam follower I1 which is located in a groove 3 of a cam block IS. The cam block I9 is mounted for rotation on a shaft 24 which constitutes the main support for the entire rod assembly. Each link l3, intermediate the pivotal connection at I6 and the cam follower at H, is pivotally attached by a pin 2| to a sleeve 22 which is mounted for rotation about the shaft 20.

A rubber boot 23 surrounds each link I3 between the pivot point at 2| and a point adjacent the wrist pin IS. The boot 23 is in the form of a flexible bellows, and closely engages the link I3 at zone 24 in a leak-proof manner. The other end of each boot 23 is provided with a collar 25 which surrounds one end of a tube 25, the other end of which is seated in an aperture in the sleeve 22. The tube 25 is provided, near its mid-point, with a radial flange 21 which is connected by bolts 2| to the body of the sleeve 22.

The purpose of the links l3 and I4 is to cause reciprocating movement of the rods I2. To this end the several links I4 are pivotally connected to the rods I2-at 23 and are also provided with cam followers designated by the numeral 30. The links I4 are each provided. with boots 3| identical in structure and function to the boots 23 just described in connection with the links I3. The pivotal connection of the links I4 to the sleeve 22 is similar to the pivotal connection described in connection with the links I3.

The reciprocating movement of the rods I2 is brought about by the rotation of the sleeve 22 relative to the shaft 20. To this end, the groove It in the cam block I3 is so cut that, upon rotation of any cam follower H for 360", that follower will be displaced in one direction for 180 of its movement and for the other 180 it will be displaced in the other direction. The nature and magnitude of this movement will be apparent upon reference to Figure 4 wherein there is shown a development of the cam groove I5. A similar groove is provided at 32 in a cam block 33 which is also mounted on the shaft 20, and the groove 32 functions in the same manner with respect to the followers as the groove l8 functions with respect to the followers I1. The two cams therefore work together on the respective followers in a manner which is made clear by reference to Figure 4 wherein the successive positions of a bar |2 are indicated in broken lines. It will be understood of course that the cam blocks I9 and 33 are fixed to the shaft 20, and, to this end, set screws 34 and 35 are provided. Intermediate the cam blocks, a spacer sleeve 36 surrounds the shaft 25.

The sleeve 22 is provided with bearings at 31 and 38 so that it can rotate about the shaft 20. The bearing 31 is mounted in a hub-like structure 39 which closes the unsupported end of the sleeve 22. The other end of the sleeve 22 is attached to a plate or disc 40, the contour of which can best be understood by reference to Figure 5. The bearings 31 and 38 turn about an axis yy of the shaft 20.

Mounted for rotation about bearings at 4| and 42, there is a sleeve 43 through which the plate III and the rods II and I2 are caused to move. The sleeve 43 is provided with a driving pulley 44 keyed thereto at 45. It is also provided with a collar at 45 having a radial flange 41 through which the collar is connected by bolts 41' to the plate III.

The shaft 20 is connected to a driving pulley 43 which is keyed thereto at 49. A supporting sleeve 50, having a bearing surface 5|, supports the sleeve 43;and the sleeve 43, through bearings 4| and 42, supports the shaft 20. An axialthrust bearing 52 is provided between the pulley 48 and the sleeve 50, this hearing 52 being keyed at 53 to the sleeve 43.

It can now be seen that rotation of the pulley 44 will cause rotation of the plate I, which in turn will cause movement of the bars II in an arcuate path concentric to the axis :ca: shown in Figure 2. It is likewise apparent that the plate Ill does not directly drive the bars l2. In order that the bars may be driven from the plate In but yet be susceptible to a considerable measure of independent movement, a gear 54 is provided which is mounted on a stud 55 iournaled in the plate In for free rotation. The gear 54 carries on its outer facean eccentric stud 56 which lies in a radial slot 51 in the plate or disc 40. The gear 54 meshes with a gear 58 which is keyed to the shaft 20.

It is now apparent therefore that, if the plate |0 moves around the shaft 20, the stud 56 acting through the slot 51 of the plate 40 will cause rotation of the sleeve 22. It is likewise apparent that the sleeve 22 is caused to move with the plate III, regardless of what the relative speed difference between the pullys 44 and 48 may be. However, although the bodily movement of the gear 54 obviously corresponds to the bodily movement of its supporting stud 55 which is mounted in the plate Ill, its individual rotation about its own axis, that is, the axis of the stud 55, depends upon the relative speed of the pulleys 44 and 48,-and consequently the driving effect between the gears 54 and 58.

It is now apparent that the movable bars l2 actually move cyclically in three separate paths and that the construction of the present invention is such that these cycles can be adjusted with respect to frequency without bringing about any difference in the predetermined phase relationships. By operation of the cam grooves l8 and 32, the bars |2 are moved back and forth or to the left and right as viewed in Figure 2. They also move as a group in and out through the reel periphery defined by the bars II, due to the fact that the bars through their plate I0 and hub 45 rotate about the axis :r-rz: while the bars I2 through the sleeve 22 and its bearings 31 and 35 rotate about the axis y--y. In addition to the back-and-forth movement of the bars and the relative eccentricity of the group of bars |2 to the group of bars II, the bars of group I2 each describe for each cycle of the movements discussed above a rotary movement between the two adjacent bars II.

It is felt that the nature of the movement of the bars II and I 2 can best be understood by a concurrent reference to Figures 5 to 12, inclusive. In referring to these figures, it simplifies the understanding of the invention to regard the shaft 20 as standing still. The reason for this is that the phenomenon described occurs cyclically as the plate 4|! gains 360 on the shaft 20. Assuming Figure 5 to be the starting position. it is noted that after the plate |ll has carried the stud 55 in a clockwise direction around the shaft 20, the gear 54 and the stud 55 carried thereby will 5 have moved 90 in a clockwise direction around the axis of the stud 55 due to the fact that gear 54 meshes with the gear 58 and both gears are of equal diameter and operate at a 1:1 ratio, Since the plate 40 is turned by the stud 56 and not by the stud 55, it is apparent that 90 of movement of-the stud 55 will bring about a movement of the plate 40 equal to 90 minus the spacing between the axes of the studs 55 and 56. Since, then, the plate It moves a full 90 with the stud 55 while the plate 48 is moved less than 90 at the same time, it is clear that the stationary bars I I, which move with the plate ID, will change their relative positions with respect to the movable bars which are carried by the sleeve 22 which is fixed to and rotates with the plate 48.

If reference is made to movable bar 12b in comparison with stationary bars I la and llb, the nature of the movement can be easily visualized. In Figure 5, movable bar I2!) is half way between stationary bars Ho and lib. In view of the lag in the movement oi. the plate 40 brought about by the partial rotation of the stud 56 about the axis of stud 55, bar In in the Figure 6 position is closer to bar Ila than it is to bar llb.

In the next 90 of movement the stud 56 of the gear 54 moves 90 clockwise about the axis of the stud 55, and consequently causes the plate 48 to gain onthe plate l exactly the same amount which it lagged the plate II] in the first 90 of movement. Thus, in Figure 7, movable bar l2b.

again lies exactly intermediate stationary bars Nb and Ila. During the next 90 of movement, as indicated in Figure 8, stud 56 again moves 90 about the axis of stud 55 and thus causes movable bar l2b to gain on stationary bar I Yb so that the spacing at 270 is the same as the spacing at 90, except that the movable bar In is close to stationary bar lib rather than close to stationary bar Ila.

From the foregoing, it can be seen that taken individually the movable bars approach and recede from the stationary bars in a complete cycle for every 360 of gain of the plate I'll ever the shaft 20. At the same time that this is occurring, the movable bars are shifting their relative radial positions with respect to the stationary bars in a manner which can best be understood by reference to Figures 9, 10, 11 and 12.

In Figures 5 and 9, the movable bar l2b which rotates about the axis 11-1.! (see Figure 2) is projecting up through the stationary bars Ila and Nb and is in thread-supporting position. In Figures 6 and 10, after 90 of movement, the movable bar I2!) is approximately the same distance from the axis :c:z: as the stationary bars I la. and lib are from the axis yy, so that the thread begins I to transfer from the movable bar to the stationary bars. In the Figures 7 and 11, the stationary bars I la and I lb are carrying the thread, and the movable bar l2b has receded within the portion of the polygon defined by the stationary bars. In

. the bars II for each 360 of gain of the sleeve 22 Figures 8 and 12 the transfer position is again over the shaft 20. The grooves l8 and ,32 are so cut that the bars are advanced toward the unsupported end of the device; that is, to the left of Figure 2 during the period while the bars I! are carrying the thread; that is, during the period from the Figure 8 position to the Figure 6 position through the Figure 5 position. On the other hand, the bars l2 are retracted or move to the right of Figure 2 during the time that the stationary bars are carrying the thread or from the Figure 6 position to the Figure 8 position through the Figure 7 position.

All of the foregoing description has been predicated on the assumption that the shaft 20 is held stationary. When this is actually done, it is perfectly apparent that the helix angle of the thread wound onthe reel will be entirely a function of the displacement caused by the cam grooves l8 and 32. However, in actual practice, the pulley 48 can be driven at some speed relative to the pulley 44. If the ratio were 1:1, a coil would be wound around the reel at the point where the thread is applied and no advancement would take place. As soon as pulley 48. is driven slower than pulley 44, thread advancement begins to occur and the helix angle can be gradually increased by decreasing the speed of pulley 48 to zero, at which time the condition illustrated will prevail. If pulley 48 is then turned in the opposite direction, it is apparent that the cycles just described can occur more than once per revolution of the plate In so that a larger helix angle can be produced and a more rapid rate of thread advancement will be possible.

The adjustability just described results from the correlation of the gear 54 and 58 so that one group of bars drives the other while both are maintained in synchronism with the eccentricityproducing elements of the apparatus.

By the use of the sleeve 22, the cams are fully protected from any corrosive treating liquids that may be carried on the thread to the threadstorage, thread-advancing device, and this general protective feature is maintained where the links l3 and I4 project through the sleeve 22 by the use of the boots such as are shown at 23.

By the use of the gear 58 meshing with the gear 54, it is possible to drive one group of bars from the other through a single driving pin such as 56 while insuring the individual circular movement of the movablebars, which is described in connection with and illustrated in Figures 5, 6, 7 and 8. In other words, the rotation of the shaft 26 relative to the sleeve 22 controls the frequency of transfer of the threads from the group of bars II to the group of bars l2. This identical movement through the cam blocks I9 and 30 controls the frequency of reciprocation of the bars I2. By the meshing of gears 58 and 54, the same relative rotation controls the frequency of the orbital movement of the bars l2. Thus, the entire device is adjustable as to frequency without requiring separate adjustment of the individual means for producin the various movements.

While this invention has been described with respect to but a single embodiment thereof, it is understood that various modifications may be 7 made on the basis of the description here afforded.

What is claimed is:

1. A thread-storage, thread advancing device comprising two similar groups of bars, a shaft, means mounting the first group for movement about a first axis within said shaft with the component bars in fixed spaced relation defining an elongate cage of polygonal cross section, means mounting the second group for movement about a second axis also within said shaft and lying eccentric but parallel to said first axis with the component bars lyin between the bars of the first group, means for rotating said first group of bars about saidshaft, means to rotate said shaft at a different rate of speed from said first group of bars, means carried by the means mounting the first group of bars and in driving relation with said shaft for driving said second group of bars about said second axis, and complementary cam means carried by said shaft and the means mounting the second group of bars to cause the component bars of the second group to move longitudinally in one direction as they move outwardly of the periphery of the bars of the first group and to move longitudinally in the other direction as they move inwardly of the periphery of the bars of the first group.

2. A'thread-storage, thread-advancing device comprising two similar groups of bars, a shaft, means mounting the first group for movement about a first axis within said shaft with the component bars in fixed spaced relation defining an elongate cage of polygonal cross section, means mounting the second group for movement about a second axis also within said shaft and lying eccentric but parallel to said first axis with the component bars lying between the bars of the first group, means for rotating said first group of bars about said shaft, a pin element, a coacting element having a slot therein, one of said elements being carried by the'means mounting the first group of bars and the other of said elements being carried by the means mounting the second group of bars so that a driving connection is established which is self-adjusting for the eccentricity of the two bar group mounting means, and complementary cam means carried by said shaft and the means mounting the second group of bars to cause the component bars of the second group to move longitudinally in one direction as they move outwardly of the periphery of the bars of the first group and to move longitudinally in the other direction as they move inwardly of the periphery of the bars of the first group.

3. A thread-storage, thread-advancing device comprising two similar groups ofbars, a shaft, means mounting the first group for movement about a first axis within said shaft with the component bars in fixed spaced relation defining an elongate cage of polygonal cross section, means mounting the second group for movement about a second axis also within said shaft and lying eccentric but parallel to said first axis with the component bars lying between the bars of the first group, means for rotating said first group of bars about said shaft, a rotatable element, means mountin said element for rotation on the means mounting the first group of bars, means for driving said element from said shaft, another element connected to the means mounting the second group of bars, one of said elements having a slot therein, a coacting pin carried by the other element. whereby a drivingconnection between the two bar-supporting means is established despite their relative eccentricity, and complementary cam means carried by said shaft and the means mounting the second group of bars to cause the component bars of the second group to move longitudinally in one direction as they move outwardly of the periphery of the bars of the first group and to move longitudinally in the other direction as they move inwardly of the periphery of the bars of the first group.

4. A thread-storage, thread-advancing device comprising two similar groups of bars, a shaft, means mounting the first group for movement about a first axis within said shaft with the component bars in fixed spaced relation defining an elongate cage of polygonal cross section, means mounting the second group for movement about a second axis also within said shaft and lying eccentric but parallel to said first axis with the component bars lying between the bars of the first group, means for rotating said first group of bars about said shaft, a first gear fixed to said shaft, second gear meshing with said first gear at a 1:1 ratio, means mountimg said second gear for rotation on the means mounting the first group of bars, an eccentric pin projecting from said second gear, a plate aflixed to the means mounting the second group of bars, said plate having a slot therein receiving said eccentric pin so that a driving connection is established between the means supporting the first group of bars and the means supporting the second group thereof, and complementary cam means carried by said shaft and the means mounting the second group of bars to cause the component bars of the second group to move longitudinally in one direction as they move outwardly of the periphery of the bars of the first group and to move longitudinally in the other direction as they move inwardly of the periphery of the bars of the first group.

5. A thread-storage, thread-advancing device comprising two similar groups of bars, a shaft,

means mounting the first group for movementabout a first axis within said shaft with the co ponent bars in fixed spaced relation defining an elongate cage of polygonal cross section; means mounting the second group for movement about a second axis also within said shaft and lying eccentric but parallel to said first axis with the g component bars lying between the bars of the first group, means for rotating said first group of bars about said shaft, means to rotate said shaft at a speed different from that at which the first group of bars is rotated, a rotatable element, means mounting said element for rotation on the means mounting the first group of bars, means for driving said element from said shaft, another element connected to the means mounting the second group of bars, one of said elements having a slot therein, a coacting pin carried by the other element, whereby a driving connection between the two bar-supporting means is established despite their relative eccentricity, and complementary cam means carried by said shaft and the means mounting the second group of bars to cause the 7 component bars of the second group to move longitudinally in one direction as they move outwardlv of the periphery of the bars of the first group and to move longitudinally in the other direction as they move inwardly of the periphery of the bars of the first group.

6. A thread-storage, thread-advancing device comprising two similar group of bars, a shaft, means mounting the first mun in! movement I about a first axis within said shaft with the component bars in fixed spaced relation defining an elongate cage of polygonal cross section, means mounting the second group for movement about a second axis also within said shaft and lying eccentric but parallel to said first axis with the component bars lying between the bars of the first group, means for rotating said first group of bars about said shaft, means to rotate said shaft at a speed different from that at which the first group of bars is rotated, a first gear fixed to said shaft, second gear meshing with said first gear at a 1:1 ratio, means mounting said second gear for rotation on the means mounting the first group of bars, .an eccentric pin projecting from said second gear, a plate afiixed to the means mounting the second group of bars, said plate having a slot therein receiving said eccentric pin so that a driving connection is established between the means supporting'the first group of bars and the means supporting the second group thereof, and complementary cam means carried by said shaft and the means mounting the second group of bars to cause the component bars of the second group to move longitudinally in one direction as they move outwardly of the periphery of the bars of the first group and to move longitudinally in the other direction as they move inwardly of the periphery of the bars of the first group.

7. A thread-storage. thread-advancing device comprising two groups of bars, a shaft, a plate mounted for rotation about a first axis within said shaft, a first group of said bars being attached to said plate and extending from one face thereof to define an elongate cage of polygonal cross section, a sleeve underlying said cage and suroun'iing a portion of said shaft, said sleeve being mounted about a second axis also within said shaft and lying eccentric but parallel to said first axis, means attached to said shaft defining a cam surface, a plurality of links each passing through said sleeve being pivotally connected thereto and coacting at one end with said cam surface and at the other end being pivotally connected to one of the bars of the second group, said links being circumferentially spaced to support the bars of the second group as a cage between the respective bars of the first group, means for rotating said plate, and means carried by said plate and in driving relation with said shaft for rotating said sleeve from said plate, the contour of said cam being such as to cause movement of the bars of the second group away from the plate during the time that the second group of bars projects beyond the periphery of the cage defined by the first group thereof and movement toward the plate as the second group of bars lies within the periphery of the cage defined by the first group thereof.

8. A thread-storage, thread-advancing device comprising two groups of bars, a shaft, a plate mounted for rotation about a first axis within said shaft, a first group of said bars being attached to said plate and extending from one face thereof to define an elongate cage of polygonal cross section, a sleeve underlying said cage and surrounding a portion of said shaft, said sleeve being mounted about a second axis also within said shaft and lying eccentric but parallel to said first axis, means attached to said shaft defining a cam surface, a plurality of links each passing through said sleeve being being pivotally connected to one of the bars of the second group, said links being circumferentially spaced to support the bars of the second group as a cage between the respective bars of the first group, resilient sealing means surrounding each link adjacent the point of pivotal connection with a bar and sealing the sleeve where the link passes therethrough, means for rotating said plate, and means carried by said plate and in driving relation with said shaft for rotating said sleeve from said plate, the contour.

of said cam being such as to cause movement of the bars of the second group away from the plate during the time that the second group of bars projects beyond the periphery of the cage defined by the first group thereof and movement toward the plate as the second group of barslies within the periphery of the cage defined by the first group thereof.

9. A thread-storage, thread-advancing device comprising two groups of bars, a shaft, a plate mounted for rotation about a first axis within said shaft, a first group of said bars being attached to said plate and extending from one "face thereof to define an elongate cage of polygonal cross section, a sleeve underlying said cage and surrounding a portion of said shaft, said sleeve being mounted about a second axis also within said shaft and lying eccentric but parallel to said first axis, means attached to said shaft defining a cam surface, a plurality of links each passing through said sleeve being pivotally connected thereto and coacting at one end with said cam surface and at the other end being pivotally connected to one of the bars of the second group, said links being circumferentlally spaced to support the bars of the second group as a cage between the respective bars of the first group, a resilient bellows surrounding each link adjacent the point of pivotal connection to a bar and extending in sealing relation to said sleeve where the link passes therethrough whereby to render the sleeve liquid tight to protect the cam surfaces and the pivot points of the links against inleakage of liquid and outleakage of lubricant, means for rotating said plate, and means carried by said plate and in driving relation with said shaft for rotating said sleeve from said plate, the contour of said cam being such as to cause movement of the bars of the second group away from the plate during the time that the second group of bars projects beyond-the periphery of the cage defined by the first group thereof and movement toward the plate as the second group of bars lies within the periphery of the cage defined by the first group thereof.

ADRIAN J. L. MORITZ.

REFERENCES arm) The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,052,125 Boos Feb. 4, 1913 2,352,868 Tarbox July 4. 1944 2,429,534 Stone Oct. 21. 1947 2,431,712 Stanley Dec. 2, 1947 2,444,071 Stanley June 29, 1948 

